Fluid pressure-driven deep-well pump



April 1969 GAISEKI YABUNO 3,438,453

FLUID PRESSUREDRIVEN DEEP-WELL PUMP Filed May 28, 1965 Sheet of e h/KEZ5 [06. 2. 1 K

MFHP/ (5752? h (5.5) (22 mama zb zzfuisz (A M150 hbfal 0) INVENT ORGA/SEK/ YnBouvo BY Q0492 0 1 9 ATTORNEYS April 15, 1969 GAISEKI YABUNO3, 53

' FLUID PRESSURE-DRIVEN DEEPWELL PUMP Filed May 28, 1965 Sheet 2 of 6F/GTZ INVENT OR 841s! A Bcuva BY t 7 9 ATTORNEYS April 15, 1969 GAISEKIYABUNO 3,438,453

FLUID PRESSURE-DRIVEN DEEP-WELL PUMP Filed May 28, 1965 Sheet 3 of eINVENT OR 4 4 5 wvo BY Qwzcm gu ATTORNEY 3 April 1969 GAISEKI YABUNO3,438,453

FLUID PRESSURE-DRIVEN DEEP-WELL PUMP Filed May 28, 1965 Sheet 4 of stffi 7b #29 avg/0r of [a #19 cos/mg 2 I To #119 exfer/or of I Y fhecasing 2 INVENTOR (Lo/earl Y4 Bawa ATTORNEYS April 1969 GAISEKI YABUNO3,438,453

FLUID PRESSURE-DRIVEN DEEP-WELL PUMP Filed May 28, 1965 Sheet 6 of6INVENTOR Game/a Y wwvo BY QZ ATTORNEYS United States Patent U.S. Cl.175102 7 Claims ABSTRACT OF THE DISCLOSURE A deep-well pump having atleast three principal elements, that is a transfer valve having acontrol valve, a reciprocating pump, and one set of six interconnectingpipes. The pipes include four pipes connected between the transfer valveand the pump and two pipes connected between the control valve and thepump. The system has three external pipes connected to the pump throughthe transfer valve that is reciprocated by action of the control valvemoving in response to movement of the pump. The three external pipesinclude a pipe for the high pressure operating fluid, a pipe for pumpingup the ground liquid and de-energized operating fluid, and an intakepipe for sucking in the ground liquid. The transfer valve controls atleast the three external pipes and the four interconnecting pipes, andis designed to withstand extremely high pressures. The pump piston mayhave a drill rod and drill head at its lower end, whereby the pumppiston will reciprocate the drill head to drill the well.

Pumping-up of a liquid from a well as deep as 3000 meters by an ordinarytype pump has been considered to be impossible because of excessiveelongation of the operating rod due to the weight of the rod itself andthe weight loaded upon the end portion of the rod. For example, a rod ofone inch in diameter and 3000 meters in length will, by itself, have aweight amounting to 13.5 tons. When equipped with fittings, the grossweight of the rod may well exceed 15 tons. In addition, when this isconsidered together with the weight of the liquid to be pumped up, itwill be readily understood by pumping-up of a liquid from such a deepwell by a pump of an ordinary type is impossible.

Various attempts have been made, therefore, to provide means toaccomplish pumping-up of ground liquid in such a deep well by the use ofliquid or pneumatic pressure. However, most of these pumps now in useare single-acting pumps with complicated mechanism, and variousdifiiculties have been encountered in actual operations. Another factorwhich constitutes a problem in deep-well pumps is the fact that thestatic pressure of a water column gains one atmospheric pressure forevery additional column of 10 meters. In a well which measures a depthof several thousand meters, the static pressure at the bottom of thewell would be several hundred atms. So far in the past, there has beenmade no consideration to provide such valves and valve seats that cancope with this enormous static pressure. Ordinary ball valves or planevalves have been used in conventional deep-well pumps to resist thepressure of several hundred atms. During operation in anultra-deep-well, it is no easy task to replace or repair the valves of apump, and therefore, valves and valve seats which are immune againststatic pressure are just what are desired, theoretically. However, itmay not be an exaggeration to say that there has been developed as yetno means to immunize valves and valve seats to meet with therequirements in actual operations. Accordingly, boring of an ultra-deepwell is still in a stage to be developed.

It is, therefore, an object of the present invention to provide adouble-acting deep-well pump to be actuated by fluid pressure which notonly perfectly satisfies such basic requirements as described above butalso renders economy and practicality. Further, the present inventioncontemplates to provide a continuously operatable boring machine unitwith a drill head attached to the lower end of the piston of the pump ofthe present invention to realize simultaneous combined performances:boring an ultra-deep well while recovering the sludge carried by thewater to the ground surface.

The primary object of the present invention is to provide a transfervalve that overcomes the above-mentionde disadvantages.

As an example, the specification describes a deep-well pump with such avalve, a cascade system employing the pump and valve combination, and adeep-Well boring device based upon the principles of the presentinvention.

The high pressure operating medium to be used in the pump of the presentinvention is a fluid which is energized on the ground. In the case ofpumping up oil, a part of the pumped-up crude oil may be used as amedium. Natural water or air which is readily available on the groundmay also be used. It has been demonstrated from practices as well asfrom experiments that in case air is used as a medium, the length oftime needed for the performance of changeover valves may be reduced, andtherefore, in certain cases, the use of air is found to be moreadvantageous.

In the pumps of the present invention, conventional plane valves or ballvalves are not used. But, indeed, a principle to realize completeimmunization against the static pressure of the water column has beendeveloped. In addition, the valves used in the pumps of the presentinvention need not be made of metal. Another feature of the presentinvention is that smooth action and a longer life of pumps is insured.Still another feature of the present invention is that the valves may bemade of a plastic material which may be either acid-proof or alkaliproofdepending upon the nature of the liquid to be pumped up.

A further object of the present invention is to provide an apparatus forpumping liquid actuatable by fluid pressure comprising a double-actingpump, a transfer valve for controlling control fluid for the pump andthe liquid to be pumped out, and control valve means for actuating thecontrol valve, said pump comprising two cylinders disposed insymmetrical relation to each other and having in common a partitionplate and a piston rod, each cylinder comprising a wall at an endopposite to said partition plate, a piston carried by said piston rod,an operating pressure fluid orifice located close to the partitionplate, a communicating pressure fluid orifice located between saidpiston and said partition plate but close to said piston at the positionwhen said piston stops at the extreme end near said wall, and aground-liquid orifice located between said piston and said wall at thesame position, whereby ground liquid is sucked in and pushed outalternately through the ground-liquid orifices respectively by themovement of the pistons in the cylinders as actuated by the pressurefluid which is alternately supplied into the cylinders through theoperating pressure fluid orifices and the communicating pressure fluidorifices.

The foregoing objects as well as other objects and advantages of thepresent invention may be more clearly understood by reference to thefollowing detailed description when considered with the drawings inwhich:

FIG. 1 of the drawings is a ground unit including a fluid pressuregenerator for a fluid pressure-driven doubleacting deep-well pump of thepresent invention;

FIGS. 2 and 3 are sectional elevations of a doubleacting pump structureprovided with valves, illustrating the principle of the presentinvention, while FIG. 2 is a somewhat schematic sectional viewillustrating the relationship between the valves, the piston and theliquid introduction orifices at the initial stage of the upwardmovement, FIG. 3 is another somewhat schematic sectional view showingthe relationship between the valves, the piston and the liquidintroduction orifices at the initial stage of the downward movement;

FIG. 4 is a somewhat schematic sectional view of an example of the pumpof the present invention, illustrating the dimensional relationshipbetween the orifices of the changeover gate valve unit and the movablevalve disc bodies;

FIGURE 5 is a sectional view of the outer cylindrical shell of the pump,with the inner moving parts and the partition plates removed, takenalong line V-V in FIG- URE 8;

FIGURES 6 and 7 are sectional views of the pump taken along lines VIVIand VIIVII in FIGURE 2,

respectively, and the difierences between the number of orifices andpipes compared with those shown in FIGURE 2 will be described in detaillater;

FIGURE 8 is a developed view of the Outer pump case and the valve takenalong line VIII-VIII in FIGURE 7;

FIGS. 9 and 10 are diagrammatic illustrations of the system in applyinga plurality of pumps of the present invention to a deep-well;

FIGS. 11 and 12 show examples of the structure of the pump for use indiscarding de-energized operating liquid outside the pump unit; and

FIG. 13 is a pump of the present invention equipped with a drill head ofa boring machine.

Now, in FIG. 1 of the drawing, numeral 1 represents a motor which drivesa liquid pressure generator 2. Numeral 3 represents a tank for storingpumped-up ground liquid. A supply pipe for a high pressure operatingmedium is represented by I2 and a pipe for pumping-up liquid isrepresented by 1 which, in the following illustrations is given toindicate a passage or pipe for pumping up the mixture of ground liquidand the de-energized operating medium. Numeral 7 represents a pipeconnecting the pressure generator 2 with the pipe [1,. Numeral 8represents a pipe for transferring liquid from the pipe 1 into the tank3. Numeral 5 represents a connecting metal fitting for bundling thepipes 11 and I and also for adding pipes. Numeral 6 represents a bufferunit for alleviating the fluctuations of the pressure in the highpressure operating medium line. Numeral 4 represents the ground surface,and numeral 9 represents the sectional view of the vertical opening of awell.

An operating medium or fluid which is highly energized by a pressuregenerator is supplied through the pipe h to the underground pumpingunit. De-energized medium, after completion of the role of sucking-upand forcing-up ground liquid, joins the pumped-up ground liquid streamand the mixture is forced upwards through the pipe to be stored in thetank 3. While h corresponds to the return path of the de-energizedoperating medium, the medium in this case joins 1 during its travel andreturns to the tank 3, and accordingly, h herein represents a phantompassage. Thus, the liquid introduction orifice 11 which connects thetank 3 with the pressure generator may be interpreted as being a pointat which the returning path of the mixture flow diverges from the pipeIn FIGS. 2 and 3 of the drawings, numeral 40 represents a cylinder for adouble-acting pump and a transfer valve unit. The portion definedbetween a lower end plate 39 and a partition plate 33 represents thedoubleacting pump, while the portion defined between the partition plate33 and an upper end plate 54 constitutes a transfer valve unit. Pipesconnecting said valve unit with said pump include six pipe linesincluding a pipe line 1,, for ground liquid in a downward pump, a pipeline l for ground liquid in an upward pump, a pipe line l1 for highpressure operating medium in a downward pump, a pipe line h for highpressure operating medium in an upward pump, an outlet pipe line s,, forthe high pressure fluid to be used for shifting the sequences of thetransfer valve unit at the terminating period of downward movement, andan outlet pipe line A for the high pressure fluid used for the operationof shifting the sequences of the transfer valve unit at the terminatingstage of upward movement. In the drawings, represents a pipe forconducting sucking up ground liquid, a pipe for pushing up groundliquid, and h an inlet pipe for con ducting the high pressure operatingmedium. In the drawings, however, the return path 12 for the operatingmedium that has been deenergized after completion of work joins l andtherefore it represents a phantom passage which is not shown in thedrawings. These four pipe lines, however, represent high pressure linesh lz and low pressure lines l l constituting four terminal pipes. Theabove-mentioned six pipes for internal communication which are disposedbetween the pump and the valve unit constitute the passages of the fluidused for effecting the changeover of the connections in conformity withthe upward and the downward movements of the pump piston by opening andclosing the valve gates interposed between the four terminal pipes andthe pump.

In FIGURES 2 and 3, the pump pistons 31, 32 that are connected togetherby rod 30 are shown in side view along with the control valves 42, 47,52, and the movable disk bodies 48, 49, 50, 51 fixed on a common axiallyextending rod 44 forming intermediate gates 55, 56, 57, S8, 59. In theactual case, the orifices, three external pipes and six interconnectingpipes are three-dimensional, but have been shown in the drawing on asingle plane in the manner of an electrical Wiring diagram for purposesof illustration.

FIGURE 8 is a development view showing the relationship between thepipes and the orifices. For example, the indication h (E E la(Z TKR)would express that the upper parts of twin segmental tubes are allocatedto the twin pipes I1 while the lower half of the same is allocated tothe twin pipes [a and there are immediately below the twin orifices Ethe twin orifices E of the pipes h, the twin orifices Z T, K, R of thetwin pipes la are in the different levels respectively. Here, the wordtwin means two substantially identical parts facing each other ondiametrically opposed sides (refer to FIGURE 8).

A description of the transfer valve, which is a key point of the presentinvention, will follow. As is clearly understood from FIGURES 5, 6, 7and 8, the outer shell of the actual device, including the transfervalve, the control valve and the pump proper, comprises two coaxialcylinders and with the vertical partition plates 61 and the transversepartition plates 62 and/or 63 in the case that the deenergized operatingfluid is to be directly discarded into the outside of the outer shellthrough the twin orifices Z Z The annular space between the cylinders 40and 60 is divided into twelve segmental tubes. If we take as twins twosegmental tubes facing each other on diametrically opposed sides, wehave then six sets of the twins around the cylinder 40. As shown inFIGURE 8, if we divide three sets of these twins by the plates 62 forthe purpose of economical usage of the annular space, we have nine twinsinto which the three external pipes and the six interconnecting pipesare assigned. The requirement on the assignment is such that: threeexternal pipes h l l and four interconnecting pipes 1,, l 11,, [1-connecting with the transfer valve comprises the twin pipesrespectively, while two interconnecting pipes S and S connecting withthe control valve comprise single pipes, respectively.

In FIGURES 5, 6, 7 and 8, there are the twins of l 1 h l respectively,two sets of twins of I1 and single pipes of 5,, and S Among threeexternal pipes,

two of the twins of I1 and the twins of 1 connected with the operatingliquid pipe 8 and the pipe for pumping up 1 in FIGURE 1 respectively andthe twins of the pipes I, connect with the ground liquid well.

Referring to FIGURE 8, the twins h have the twins of the orifices G, Iand Q, and the single orifice D for the control valve; the two twins hhave the twins of the orifices E E the twins l have the twins of theorifices Z U, L, S; the twins have the twins of the orifices Y Y thetwins have the twins of the orifices J 1 the twins h have the twins ofthe orifices F, H and P, and the single orifice C for the control valve;the twins l have the twins of the orifices Z T, K, R. Single pipe 5,,has the single orifice A and the single orifice M, and the single pipe Shas the single orifice B and the single orifice N.

The orifices may be classified as four kinds: A, B, C, D (each of thembeing a single orifice) for the control valve; sixteen kinds G, E F, EH, Z I, Z U, Y T, Y K J L, 1 (each of them being twins) for the transfervalve; and six kinds S, N, Q, P, M, R (each of them being twins exceptsingle orifices N and M) for the pump proper. These orifices are, as inFIGURE 8, arranged in each pipe, and on each different level, while theorifices of the transfer valve being combined as G-Ez, FE1, H-Z I-Zg,U-Y2, T-Y K-J L-J2 are arranged on each of eight different levels and atregular intervals. And, when these combined orifices are engaged withthe disks of the movable disk body of the transfer valve, this resultsin the disconnection between the external pipe and the interconnectingpipe. When these orifices are engaged with the gates. it results in theinterconnection between them.

The movable disk body of the transfer valve comprises disks 48-51forming the gates 55, 56, 57, 58, 59 at regular intervals and mounted onthe axially extending rod 44 common with the axis of the control valve.

Thus, the transfer valve comprises said cylindrical shell with saidconnected orifices, and said movable disk body.

The control valve built in the common cylindrical shell comprises theorifices A, B, C, D; the pistons 52, 47, 42 which are fixed with the rod44 common with that of the transfer valve, the chamber 53 between theend plate 54 and the piston 52, the chamber 46 between the plate 45 andthe piston 47, the chamber 43 between the plate 45 and the piston 42,and the chamber 41 between the piston 42 and the plate 33. In thisvalve, it is noticed that the diameter of the piston 52 or 47 is largerthan that of the piston 42.

The movable disk body of the transfer valve is put in reciprocatingmotion with a definite stroke by the piston of the control valve. Whilethe four groups of the combined orifices FE IZ T-Y and L-J are closed bythe disks 51, 50, 49 and 48 respectively, another four groups of thecombined orifices GE HZ U-Y and K-J are connected by the gates 59, 58,57 and 5-6 respectively, and vice versa.

Again returning to FIGS. 2 and 3, the portion on each side of thepartition plate 36 represents a single acting pump capable of makingupward and downward movement, respectively. Numerals 31 and 32 representdownward and upward pistons, respectively. Numeral 30 represents apiston rod for connecting said pistons. P and Q represent orifices forforcing-in a high pressure operating medium for effecting downward orupward movement, respectively. Likewise, R and S represent an outlet andan inlet of ground liquid. Similarly, M and N represent liquidintroduction orifices for transmitting a part of the operating pressureto the control valve when said piston has reached the position ofterminating movement. Numerals 34 and 35 represent chambers forpumped-up liquid, and likewise, numerals 37 and 38 represent chambersfor high pressure operating fluid.

In FIG. 4 is shown an example of actual structure in which an extraopening a is given. However, this extra opening should not give rise tosaid undesirable intercommunication between the high pressure system andthe low pressure system. In the drawing, the diameter of the orifice F-Eis given a dimension of d -l-a as against the diameters d for all theother orifices, and among the movable valve disc bodies 48, 49, 50 and51, three valve disc bodies other than 50 are given a uniform thicknessof 2' while the valve disc body 50 is given the thickness of z -i-a,wherein this a represents the amount left out of the overlap of theorifice and the valve disc. This discrepancy in the diameters is givento prevent the intercommunication between the orifice FE which has adiameter elongated by a and the low pressure orifice I-I-Z which iscommunicated by an interconnecting pipe 11,; in other words, thedimensional discrepancy is provided to satisfy the requirement that atthe starting of opening of the orifice F-E at least the orifice H-Z,must complete closing. Hence, the necessity that while all of the fivegates except the gate 58 are equally of a height d the gate 58 aloneshould have a height: d a=d In this drawing, there is shown an examplein which the range of the stroke w is designed to be consistent with theheight t FIG. 2 shows an initial stage of an upward movement, and thehigh pressure operating fluid pushes up the piston 32 in the order of h-E G-]z Q. The ground liquid in the chamber 35 is forced upward in theorder of Sl UY -l The operating liquid which wa energized and which isnow de-energized joins the ground liquid and is forced upward in theorder of P-h,,I-IZ Z UY Also, ground liquid is sucked into the chamber34 by the reverse route of RI -KJ -1 Now, let us consider the action ofthe valves at this moment. Because the pipe line h alone is beingenergized under a high pressure, the passage between the orifice D andthe chamber 43 of a control valve gets energized so that the movablevalve disc body ma be held at a lower position. When the piston 32reaches the position of ending movement, intercommunication between Q-Ntakes place, thereby imposing a pressure upon the piston 47 of saidcontrol valve in the order of S B46. At this moment, the chamber 43 isbeing subjected to a pressure as described above, but, owing to the factthat the diameter of the piston 47 is larger than that of the valvepiston 42, said piston 47 will start an upward movement. This willreverse the opening and closing action of the orifices GE and F-E andwill cause the pipe line h to be de-energized while the tubular passageor pipe h is energized. This is followed by the energization of thechamber 41. Thus, the valve disc bodies complete their upward movementsand hold this state. This position is shown in FIG. 3. The opening andclosing sequences of the orifices of the transfer valve are shifted, andthe pump pistons start a downward movement. More particularly, theorifice P is energized to push the piston 31 downwards. The descriptionof the displacement of the liquid in each of the chambers of the pump atthis moment is omitted, since the movement of the liquid will beapparent from the drawings when considered together with the previousdescription concerning the upward movement of the liquid. When the pumppiston reaches the ultimate end of the downward movement, a pressurewill be transmitted into the chamber 53 in the order of PMS,,-A53, andthe valve disc body will move downwards to return to the state as shownin FIG. 2, to be followed by the starting of upward movement of thepiston 32. Thus, so long as the high pressure operating fluid hcontinues to be energized, the pump will repeat its reciprocatingmovements, thereby accomplishing the continuous pumping-up of liquid asaimed at.

As described above, for a transfer valve unit of a double-acting pumpwhich pumps up ground liquid by the use of a high pressure operatingmedium, it is theoretically necessary that the four terminal pipes,namely, the outlet and inlet pipes I1 and I2 for the high pressuremedium, the pipe 1 for sucking up ground liquid, and the pipe I forpumping up ground liquid are connected with said transfer valve. In thecase where a liquid similar in quality with the ground liquid is used asa high pressure operating medium, however, said four passages or pipesmay be reduced to three by utilizing the pipe line of pumpingup groundliquid as the return path of the operating medium. Also, in case water,air, etc. is used as a high pres sure operating medium, it is easy toarrange the structure so that such medium may be discarded outside thepump immediately after being de-energized, if required. To describe thisin more detail, in the case, for example Where water is abundantlyavailable on the ground and where such water is used as an operatingfluid, the deenergized water which has finished the role as highpressure operating fluid should be discarded outside the pump byinsulating the passages H-Z and 1-2 of the transfer valve by the upperpartition plate 62 and a lower partition plate 63 from the pipes 11 land l as shown in FIGS. 11 and 12. Also, in utilizing compressed air, orwhen the pumps of the present invention are used in cascade form, theremay be cases where it is desirable from the structural point of view todiscard the operating fluid immediately after being de-energized in themanner as described above.

Next, the cascade arrangement of the pumps of the present invention willbe described. In case of a well having a depth as great as 3000 meters,the high pressure operating medium requires to be given a pressure of atleast several hundred atms. This will mean that every portion of theentire unit becomes costly. Whereas, if the pumps of the presentinvention are used in cascade, meaning that by dividing the overallheight of a well into equal parts numbering n, and by placing at eachpoint of the division one pump made of a material which can resist thepressure of l/n of the overall height, by arranging each pump invertical cascade form, by connecting a pressure inlet pipe of each pumpwith the main high pressure operating fluid supply pipe extending fromthe fluid source, and also by connecting a suck-up pipe of any pump witha push-up pipe of another pump just below said any pump there isprovided a great advantage that every portion of the overall unit hasonly to resist a low pressure. FIGS. 9 and 10 connote this principle.FIG. 9 illustrates the principle of the pump of the present invention,wherein V denotes a valve; P a pump; and 61C six internal communicationpipes i.e. four interconnecting pipes and two communicating pipes. Sincethis pump has four terminal pipes: h I1 1 and 1 as described in theabove, if the push-up pipe of an arbitrary pump among the pumpsnumbering n is connected with the sucking pipe 1 of the adjacent pumplocated above said arbitrary pump, and if pumps numbering n areconnected in vertical cascade form, and also if de-energized liquidwhich has completed work is designed to be directly discarded outsidethe pump in such manner as is illustrated in FIGS. 11 and 12, a pump foran ultra-deep Well can work without being exposed to an enormousexternal static pressure.

Next, the pump of the present invention equipped with boring head willbe described with reference to FIG. 13.

In FIG. 13, a drill rod 65 and a drill head 66 are attached to the lowerend of the piston 31. By the action of the piston which is operated bythe liquid pressure, the drill is operated. The drill thus will proceeddeeper into the ground. The sludge produced by the drilling can becarried up to the ground by the ground liquid. On the other hand, it iseasy to mechanically or electrically check or detect the amount ofboring relative to the fixed position on the ground where the pump unitis located.

Therefore, when the detector senses that a predetermined depth has beendrilled, the pump can be lowered to the level attained by the boring,and thus continuous boring of the well can be attained. By repeatingthis operation either manually or by suitable automatic means,continuous well-boring operation can be realized. In this case, it isalso possible from practical point of view to conduct the pushing-up ofground liquid by the action of the piston 32 alone, without the endplate 39 and the liquid introduction orifices R, K and T associatingwith the pipe line 1,, for example, among the communicating pipe lines 1and l It is to be understood that various modifications may be conceivedwithout departing from the substantial properties of the presentinvention. The above described examples are intended merely toillustrate some of the important aspects in certain selected embodimentsof the present invention.

What is claimed is:

1. An apparatus for pumping liquid actuatable by fluid pressurecomprising a double-acting pump, a transfer valve means for controllingcontrol fluid for the pump and the liquid to be pumped out, and controlvalve means for actuating the transfer valve means; said pump comprisingtwo cylinders disposed in symmetrical relation to each other and havingin common a partition plate and a piston rod; each cylinder comprising awall at an end opposite to said partition plate, a piston carried bysaid piston rod, an operating pressure fluid orifice located close tothe partition plate, a exhausting pressure fluid orifice located betweensaid piston and said partition plate but close to said piston at theposition when said piston stops at the extreme end near said wall, and aground-liquid orifice located between said piston and said wall at thesame position; said transfer valve unit consisting of a cylinder, a rod,a group of disk bodies carried by said rod and spaced from each other atpredetermined intervals, a plurality of gates formed by the spacesbetween said disk bodies, a plurality of orifices disposed in thecylinder; said control valve mean-s having a cylinder, a piston in saidcylinder, a wall between said control valve means and said transfervalve means, and a piston rod drivingly connected to and extendingintegrally from said transfer valve rod through said wall providedbetween said transfer valve and said control valve; said apparatusfurther comprising four terminal pipe means consisting of two pipe meansfor conducting high pressure operating fluid, pipe means for conductingsucked up ground liquid and pipe means for conducting pushed outdischarged ground liquid, each of said pipe means being connected withsaid transfer valve means; two ground liquid interconnecting pipe meansconnecting respectively said ground liquid orifices with said transfervalve means, two operating fluid interconnecting pipe means respectivelyfluid connecting said operating pressure fluid orifices with saidtransfer valve means; and two exhaust fluid pipe means providing fluidcommunication between said exhausting pressure fluid orifices,respectively, and said transfer valve means.

2. An apparatus according to claim 1, wherein said transfer valve meansorifices include two high pressure operating fluid orifice means, onepair of which are slightly larger in the axial dimension, with respectto said transfer valve means rod, than the other pair, and both pairsbeing connected with said two pressure fluid interconnecting pipe means;said transfer valve disk bodies including one disk body means forcontrolling the exhaust operating fluid and being slightly larger in theaxial dimension than the other disk bodies, to constitute means forclosing one pair of orifice means for the high pressure operating fluidimmediately prior to opening the other pair of orifice means for thehigh pressure operating fluid.

3. A pump, comprising: fluid operated pump means; a transfer valvehaving a cylinder with a plurality of orifices, a plurality of disksslideably arranged in said cylinder for valving said orifices and a roddrivingly connecting said disks; three external pipe means fluidcommunicating with corresponding orifices and six interconnecting pipemeans for providing fluid communication between corresponding orificesand said pump means, each of said :pipe means and corresponding orificesincluding substantially identical pipes and orifices diametricallydisposed on opposite sides of said cylinder; said orifices beingarranged, in planes generally perpendicular to said rod, to providefluid communication between corresponding ones of said external pipeorifices and said internal pipe orifices, respectively; said disks beingspaced on said rod at axial distances substantially equal to the axialdistances between said planes; said orifices and said disks being spacedaxially from each other so that at one axial position of said disks onehalf of said external pipe orifices will be fluid connected with thecorresponding one half of the interconnecting pipe orifices, and atanother axial position of said disks the other half of said externalpipe orifices will be connected with the other half of saidinterconnecting pipe orifices.

4. The device of claim 3, including control valve means for shiftingsaid disks axially between said two positions, including wall means andpiston means forming two piston-cylinder chambers of relatively largeeffective cross section and two piston-cylinder chambers of relativelysmall effective cross section; said transfer valve means having fourorifices connected respectively with said cylinders; said piston meansbeing drivingly connected to said transfer valve means for relativelyshifting said disks; said pump means being a double acting pumpreciprocalable between two positions corresponding to the reversal ofdirection; said transfer valve selectively supplying operating fluid toboth one of said relatively small chambers for urging said transfervalve means in one direction and said pump means for driving said pumpmeans in one direction toward one of its positions, and for supplyingoperating fluid to both the other of said small chambers for urging saidtransfer Valve means in its other direction and said pump means fordriving said pump means in the other direction toward the other of itspositions; valve means responsive to the position of said pump means forsupplying operating fluid to one of said relatively large chambers fordriving said transfer valve means in its said other direction when saidpump means is closely adjacent to its said one position and forsupplying operating fluid to the other of said relatively large chambersfor driving said transfer valve means in its one direction when saidpump means is closely adjacent to its said other position.

5. The device of claim 4, wherein said transfer valve means isoperatively fluid interposed between said pump means and said threeexternal pipe means; one of said external pipe means supplying operatingfluid, the second of said external pipe means delivering the liquidpumped by said pump means and the third of said external pipe meansproviding the suction liquid for said pump means.

6. The device of claim 5, including at least one additional set of pumpmeans, transfer valve means and control valve means substantiallyidentical to a first set of said first mentioned pump means, transfervalve means and control valve means; said sets being serially arrangedwith one of the outermost sets having its delivering external pipe meansbeing for connecting to a reservoir, the other outermost set having itssuction external pipe means being for connection to a source of fluid tobe pumped, the remaining delivering external pipe means being connectedto the remaining suction external pipe means, respectively, of adjacentsets, and said operating fluid external pipe means being connected inparallel.

7. The device of claim 5, wherein said pump means has a piston andpiston rod; and including a drill head drivingly connected to said pumpmeans piston rod to pump up the sludge that issues from the drilling,together with the ground liquid and any liquid poured from the groundsurface into the well bottom.

References Cited UNITED STATES PATENTS 1,140,939 5/1915 Bailey l03461,714,425 5/1929 Knab l0346 2,022,781 12/1935 Pigott 103-46 2,624,2851/1953 Hall 103-46 2,629,329 2/1953 Rose et a1. 103-156 X 2,948,2248/1960 Bailey et a1 l0346 2,949,857 8/1960 Coberly l0352 3,162,13312/1964 Smith l0352 OTHER REFERENCES A.P.C., Application of Shinomiya,Ser. No. 399,916, -102, published May 25, 1943.

CHARLES E. OCONNELL, Primary Examiner.

JAN A. CALVERT, Assistant Examiner.

US. Cl. X.R. 103-46, 52

